US3598507A - Fuel injection pump for multicylinder internal combustion engines - Google Patents
Fuel injection pump for multicylinder internal combustion engines Download PDFInfo
- Publication number
- US3598507A US3598507A US22883A US3598507DA US3598507A US 3598507 A US3598507 A US 3598507A US 22883 A US22883 A US 22883A US 3598507D A US3598507D A US 3598507DA US 3598507 A US3598507 A US 3598507A
- Authority
- US
- United States
- Prior art keywords
- pump
- distributor
- cylinder bore
- radial cylinder
- pump piston
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 239000000446 fuel Substances 0.000 title claims abstract description 49
- 238000002347 injection Methods 0.000 title claims abstract description 17
- 239000007924 injection Substances 0.000 title claims abstract description 17
- 238000002485 combustion reaction Methods 0.000 title claims description 9
- 238000006073 displacement reaction Methods 0.000 claims description 10
- 230000000737 periodic effect Effects 0.000 claims description 6
- 230000010363 phase shift Effects 0.000 abstract description 4
- 230000000712 assembly Effects 0.000 abstract description 2
- 238000000429 assembly Methods 0.000 abstract description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 1
- 208000015181 infectious disease Diseases 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
- F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
- F02M41/14—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons
- F02M41/1405—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
- F02M59/366—Valves being actuated electrically
Definitions
- This invention relates to a fuel injection pump for multicylinder internal combustion engines and is of the type wherein the infection of fuel is effected by at least one reciprocating pump piston disposed in a radial bore of a rotary pump body which simultaneously serves as a distributor. For executing a delivery or pressure stroke, the piston is urged inwardly by a cam and, for executing its suction stroke, the piston is exposed to fuel pressure generated by an upstream arranged delivery pump forcing fuel through a controlled channel associated with said cylinder bore.
- the fuel quantities to be injected are determined by means of a throttle which, dependent upon the pressure and the flow passage section, allows a certain fuel quantity per time unit to flow through.
- fuel injection pumps wherein the fuel quantities to be injected are controlled by means of a solenoid valve which operates on electronic command.
- An electronic regulator permits a more accurate matching of the fuel quantities to be injected with the torque characteristics of the engine and is less expensive than a mechanical or hydraulic regulator
- Fuel injection pumps of this type are disadvantageous in that the opening and the closing periods of the magnetic valve are relatively long (approximately 1 millisecond each). In a 3,000 rpm. pump during each such period the driving cam rotates approximately 18, or 36 for an opening and successive closing step. It follows that for each revolution of the distributor only two pressure strokes may be performed if a sufficiently large regulating range is to remain available.
- the rotary distributor of a radial fuel injection pump houses at least two pump units operating with a phase shift.
- Each pump unit has a pump work chamber and channel means connecting said pump work chamber with a common fuel supply means, such as a sole suction chamber.
- Each channel means is opened or closed by a solenoid valve, one associated with each pump unit.
- FIG. 1 is an axial section view ofa radial fuel injection pump according to the invention taken along line l-I of FIG. 2;
- FIG. 2 is a sectional view along line Il-II ofFlG. I;
- FIG. 3 is a diagram showing the displacement of the pistons as a function ofthe angular position ofthe pump drive shaft.
- a distributor 2 which rotates in tune with an internal combustion engine (not shown) associated with the fuel injection pump.
- the distributor 2 has an enlarged portion serving as a distributor head rotates, cams 7 and 7' cause the respective piston pairs 6 and 6' to execute their inwardly directed pressure or delivery strokes. Following each delivery stroke, the outward motion of the pistons 6, 6' towards cam rings 7, 7 (suction stroke) is caused by centrifugal forces and by the pressure of the fuel flowing into the pump work chamber of pistons 6 and 6.
- Each cam ring 7, 7 has two rising cam face portions 8, 8' so that each piston pair 6, 6' executes two pressure strokes and two suction strokes for each revolution of the distributor 2.
- the first pump unit formed of bore 4 and pistons 6 is hydraulically completely separated from the second pump unit formed for bore 5 and pistons 6'.
- the pump. work chamber of the first pump unit is, during its pressure stroke, connected with a pressure channel 11' through an axial bore 10 and a distributor bore 11, both provided in the distributor 2.
- a pressure conduit (not shown) leading to the internal combustion engine.
- fuel under pressure flows from a suction chamber 12 across a bore 13 into an annular groove 14 provided in the housing 1.
- the annular groove 14 is in continuous communication with the pump work chamber. of the first pump unit through a radial bore 15 of the distributor 2 and the axial bore 10.
- the suction chamber 12, provided in the pump housing 1, is supplied with fuel by means of a delivery pump, not shown.
- the bore 13 is controlled by a solenoid valve 16. As long as the solenoid valve 16 is open, the fuel may flow from the suction chamber 12 into the pump work chamber of the first pump unit 4, 6.
- the pump work chamber of the second pump unit 5, 6 is connected by means of a longitudinal channel 18 provided in the distributor 2 with a distributor bore 19 which, during the pressure stroke of the pump pistons 6', communicates with a pressure channel 20 to which there is attached a pressure conduit (not shown) lead ing to the internal combustion engine.
- each pumpunit there are provided two pressure channels 20 and two pressure channels 11 (only one of each shown).
- the longitudinally extending bore 18 is connected with an annular groove 21 provided in the outer lateral face of the distributor 2.
- the annular groove 21 is in continuous communication with a bore 23 leading to the suction chamber 12 and controlled by a solenoid valve 22.
- the solenoid valves 16 and 22 are so designed that they are open when unenergized. Their movable valve member (designated at 24 in solenoid valve 22) is pressed against its valve seat into a closed position by the fuel pressure prevailing in the pump work chambers during pressure strokes. On the other hand, during suction strokes, the fuel flowing from the suction chamber 12 to the pump work chamber, aids the valve opening spring 25 of each solenoid valve in displacing the valve member 24 into an open position. Thereafter, as soon as an electronic control device (not shown) energizes the coil 26 of the solenoid valve, the valve member 24 is pulled into its seat by means of an armature 27. 1
- FIG. 3 there is graphically shown the operation of the fuel injection pump described hereinabove.
- the displacement s of the pump pistons 6, 6' (ordinate) is shown as a function of the rotational angle a of the distributor 2 (abscissa).
- the displacement of the pistons 6 operating in the bore 4 first pump unit
- the displacement of the pistons 6' operating in the bore 5 second pump unit.
- a comparison of these graphs shows that the two pump units operate with a phase shift of Expressing one pumping cycle in degrees of distributor rotation, it is thus seen that one pumping cycle is divided into 30 for a delivery stroke, 140 for a suction stroke and for changing channels.
- the solenoid valves 16 and 22 may open the respective bores 13 and 23 connecting the suction chamber 12 with the pump work chambers of the pump units, immediately after closing the pressure channels 11 and 20, respectively. in this manner, the solenoid valves are already open when the suction stroke begins. Consequently, the fuel quantities to be delivered by the pump are affected only by the closing characteristics of the solenoid valve and not by the opening characteristics thereof.
- the periods, during which fuel quantity control may take place by virtue of closing the channels 13 and 23 by the solenoid valves 16 and 22, are represented by lines drawn parallel below the two abscissae in FIG. 3.
- a fuel injection pump associated with a multicylinder internal combustion engine and being of the known type that includes (A) a rotary distributor, (B) radial pump means contained in said distributor and (C) stationary cam means operatively connected with said radial pump means to cause it to perform pressure strokes, the improvement comprising,
- A. a first pump unit including 1. a first radial cylinder bore provided in said distributor, 2. at least one first pump piston reciprocably disposed in said first radial cylinder bore,
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
In a fuel injection pump including a rotary distributor with radially operating pump pistons, in order to increase the total number of delivery strokes, said distributor houses two radial pump assemblies supplied by a sole suction chamber and operating with a phase shift of 90*.
Description
United States Patent I l l Inventors Appl No,
Priority FUEL INJECTION PUMP FOR MULTICYLINDER INTERNAL COMBUSTION ENGINES Willi Volt; [5 l Int. Cl F04b 7/00 Ulrich Aldi ge bo f S ut g [50] Field of Search. 417/505, Germany 485v 385. 387. 52L 533: 123/139 E 22.883
I i. 23 E W 16 1g 1 FUEL INJECTION PUMP F OR MULTICYLINDER INTERNAL COMBUSTION ENGINES BACKGROUND OF THE INVENTION This invention relates to a fuel injection pump for multicylinder internal combustion engines and is of the type wherein the infection of fuel is effected by at least one reciprocating pump piston disposed in a radial bore of a rotary pump body which simultaneously serves as a distributor. For executing a delivery or pressure stroke, the piston is urged inwardly by a cam and, for executing its suction stroke, the piston is exposed to fuel pressure generated by an upstream arranged delivery pump forcing fuel through a controlled channel associated with said cylinder bore.
In a known fuel injection pump of the aforenoted type (such as disclosed in German Pat. No. 1,288,359), the fuel quantities to be injected are determined by means of a throttle which, dependent upon the pressure and the flow passage section, allows a certain fuel quantity per time unit to flow through.
Further, fuel injection pumps are known, wherein the fuel quantities to be injected are controlled by means ofa solenoid valve which operates on electronic command.
An electronic regulator permits a more accurate matching of the fuel quantities to be injected with the torque characteristics of the engine and is less expensive than a mechanical or hydraulic regulator Fuel injection pumps of this type are disadvantageous in that the opening and the closing periods of the magnetic valve are relatively long (approximately 1 millisecond each). In a 3,000 rpm. pump during each such period the driving cam rotates approximately 18, or 36 for an opening and successive closing step. It follows that for each revolution of the distributor only two pressure strokes may be performed if a sufficiently large regulating range is to remain available.
OBJECTS AND SUMMARY OF THE INVENTION It is an object of the invention to provide an improved fuel injection pump of the aforenoted type which has a simplified structure particularly adapted for incorporating electronically operated solenoid valves to control the fuel quantities to be delivered.
It is another object of the invention to provide an improved fuel injection pump of the aforenoted type which permits more than two pressure strokes per revolution.
Briefly stated, according to the invention, the rotary distributor of a radial fuel injection pump houses at least two pump units operating with a phase shift. Each pump unit has a pump work chamber and channel means connecting said pump work chamber with a common fuel supply means, such as a sole suction chamber. Each channel means is opened or closed by a solenoid valve, one associated with each pump unit.
The invention will be better understood and further objects and advantages of the invention will become more apparent from the ensuing detailed specification of a preferred, although exemplary embodiment taken in conjunction with the drawing.
BRIEF DESCRIPTION OF THE DRAWING FIG. 1 is an axial section view ofa radial fuel injection pump according to the invention taken along line l-I of FIG. 2;
FIG. 2 is a sectional view along line Il-II ofFlG. I; and
FIG. 3 is a diagram showing the displacement of the pistons as a function ofthe angular position ofthe pump drive shaft.
DESCRIPTION OF THE EMBODIMENT In a two part pump housing I there is disposed a distributor 2 which rotates in tune with an internal combustion engine (not shown) associated with the fuel injection pump. The distributor 2 has an enlarged portion serving as a distributor head rotates, cams 7 and 7' cause the respective piston pairs 6 and 6' to execute their inwardly directed pressure or delivery strokes. Following each delivery stroke, the outward motion of the pistons 6, 6' towards cam rings 7, 7 (suction stroke) is caused by centrifugal forces and by the pressure of the fuel flowing into the pump work chamber of pistons 6 and 6. Each cam ring 7, 7 has two rising cam face portions 8, 8' so that each piston pair 6, 6' executes two pressure strokes and two suction strokes for each revolution of the distributor 2. The first pump unit formed of bore 4 and pistons 6 is hydraulically completely separated from the second pump unit formed for bore 5 and pistons 6'. The pump. work chamber of the first pump unit is, during its pressure stroke, connected with a pressure channel 11' through an axial bore 10 and a distributor bore 11, both provided in the distributor 2. To the pressure channel 11 there is connected a pressure conduit (not shown) leading to the internal combustion engine. During the suction stroke of pistons 6, fuel under pressure flows from a suction chamber 12 across a bore 13 into an annular groove 14 provided in the housing 1. The annular groove 14 is in continuous communication with the pump work chamber. of the first pump unit through a radial bore 15 of the distributor 2 and the axial bore 10. The suction chamber 12, provided in the pump housing 1, is supplied with fuel by means of a delivery pump, not shown. The bore 13 is controlled by a solenoid valve 16. As long as the solenoid valve 16 is open, the fuel may flow from the suction chamber 12 into the pump work chamber of the first pump unit 4, 6.
Similarly to the first pump unit 4, 6, the pump work chamber of the second pump unit 5, 6 is connected by means ofa longitudinal channel 18 provided in the distributor 2 with a distributor bore 19 which, during the pressure stroke of the pump pistons 6', communicates with a pressure channel 20 to which there is attached a pressure conduit (not shown) lead ing to the internal combustion engine.
Corresponding to the two pressure strokes executed per revolution by each pumpunit, there are provided two pressure channels 20 and two pressure channels 11 (only one of each shown). The longitudinally extending bore 18 is connected with an annular groove 21 provided in the outer lateral face of the distributor 2. The annular groove 21 is in continuous communication with a bore 23 leading to the suction chamber 12 and controlled by a solenoid valve 22.
The solenoid valves 16 and 22 are so designed that they are open when unenergized. Their movable valve member (designated at 24 in solenoid valve 22) is pressed against its valve seat into a closed position by the fuel pressure prevailing in the pump work chambers during pressure strokes. On the other hand, during suction strokes, the fuel flowing from the suction chamber 12 to the pump work chamber, aids the valve opening spring 25 of each solenoid valve in displacing the valve member 24 into an open position. Thereafter, as soon as an electronic control device (not shown) energizes the coil 26 of the solenoid valve, the valve member 24 is pulled into its seat by means of an armature 27. 1
Turning now to FIG. 3, there is graphically shown the operation of the fuel injection pump described hereinabove. In the diagram, the displacement s of the pump pistons 6, 6' (ordinate) is shown as a function of the rotational angle a of the distributor 2 (abscissa). In the upper graph there is shown the displacement of the pistons 6 operating in the bore 4 (first pump unit) while in the lower graph there is depicted the displacement of the pistons 6' operating in the bore 5 (second pump unit). A comparison of these graphs shows that the two pump units operate with a phase shift of Expressing one pumping cycle in degrees of distributor rotation, it is thus seen that one pumping cycle is divided into 30 for a delivery stroke, 140 for a suction stroke and for changing channels. Thus, the solenoid valves 16 and 22 may open the respective bores 13 and 23 connecting the suction chamber 12 with the pump work chambers of the pump units, immediately after closing the pressure channels 11 and 20, respectively. in this manner, the solenoid valves are already open when the suction stroke begins. Consequently, the fuel quantities to be delivered by the pump are affected only by the closing characteristics of the solenoid valve and not by the opening characteristics thereof. The periods, during which fuel quantity control may take place by virtue of closing the channels 13 and 23 by the solenoid valves 16 and 22, are represented by lines drawn parallel below the two abscissae in FIG. 3.
What we claim is:
1. In a fuel injection pump associated with a multicylinder internal combustion engine and being of the known type that includes (A) a rotary distributor, (B) radial pump means contained in said distributor and (C) stationary cam means operatively connected with said radial pump means to cause it to perform pressure strokes, the improvement comprising,
A. a first pump unit including 1. a first radial cylinder bore provided in said distributor, 2. at least one first pump piston reciprocably disposed in said first radial cylinder bore,
B. a first cam associated with said first pump piston to cause periodic inward displacement thereof upon rotation of said distributor, C. a fuel source, D. a first channel connecting said first radial cylinder bore with said fuel source, E. a first solenoid valve associated with said first channel to control the flow of fuel therethrough, F. at least one second pump unit including 1. a second radial cylinder bore provided in said distributor, said second radial cylinder bore extending spaced from said first radial cylinder bore, the axes of said first and second radial cylinder bores lying in parallel planes,
2. at least one second pump piston reciprocably disposed in said second radial cylinder bore,
G. a second cam associated with said second pump piston to cause periodic inward displacement thereof upon rotation of said distributor,
H. a second channel connecting said second radial cylinder bore with the same said fuel source,
I. a second solenoid valve associated with said second channel to control the flow of fuel therethrough and J. means causing said first pump piston to reciprocate outof-phase with respect to said second pump piston.
2. An improvement as defined in claim 1, wherein the axes of said first and said second radial cylinder bores are disposed at an angle of with respect to one another.
Claims (4)
1. In a fuel injection pump associated with a multicylinder internal combustion engine and being of the known type that includes (A) a rotary distributor, (B) radial pump means contained in said distributor and (C) stationary cam means operatively connected with said radial pump means to cause it to perform pressure strokes, the improvement comprising, A. a first pump unit including 1. a first radial cylinder bore provided in said distributor, 2. at least one first pump piston reciprocably disposed in said first radial cylinder bore, B. a first cam associated with said first pump piston to cause periodic inward displacement thereof upon rotation of said distributor, C. a fuel source, D. a first channel connecting said first radial cylinder bore with said fuel source, E. a first solenoid valve associated with said first channel to control the flow of fuel therethrough, F. at least one second pump unit including 1. a second radial cylinder bore provided in said distributor, said second radial cylinder bore extending spaced from said first radial cylinder bore, the axes of said first and second radial cylinder bores lying in parallel planes, 2. at least one second pump piston reciprocably disposed in said second radial cylinder bore, G. a second cam associated with said second pump piston to cause periodic inward displacement thereof upon rotation of said distributor, H. a second channel connecting said second radial cylinder bore with the same said fuel source, I. a second solenoid valve associated with said second channel to control the flow of fuel therethrough and J. means causing said first pump piston to reciprocate out-ofphase with respect to said second pump piston.
2. at least one first pump piston reciprocably disposed in said first radial cylinder bore, B. a first cam associated with said first pump piston to cause periodic inward displacement thereof upon rotation of said distributor, C. a fuel source, D. a first channel connecting said first radial cylinder bore with said fuel source, E. a first solenoid valve associated with said first channel to control the flow of fuel therethrough, F. at least one second pump unit including
2. at least one second pump piston reciprocably disposed in said second radial cylinder bore, G. a second cam associated with said second pump piston to cause periodic inward displacement thereof upon rotation of said distributor, H. a second channel connecting said second radial cylinder bore with the same said fuel source, I. a second solenoid valve associated with said second channel to control the flow of fuel therethrough and J. means causing said first pump piston to reciprocate out-of-phase with respect to said second pump piston.
2. An improvement as defined in claim 1, wherein the axes of said first and said second radial cylinder bores are disposed at an angle of 90* with respect to one another.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19691919707 DE1919707A1 (en) | 1969-04-18 | 1969-04-18 | Fuel injection pump for multi-cylinder internal combustion engines |
Publications (1)
Publication Number | Publication Date |
---|---|
US3598507A true US3598507A (en) | 1971-08-10 |
Family
ID=5731570
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US22883A Expired - Lifetime US3598507A (en) | 1969-04-18 | 1970-03-26 | Fuel injection pump for multicylinder internal combustion engines |
Country Status (4)
Country | Link |
---|---|
US (1) | US3598507A (en) |
DE (1) | DE1919707A1 (en) |
FR (1) | FR2045502A5 (en) |
GB (1) | GB1310386A (en) |
Cited By (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4083346A (en) * | 1975-01-28 | 1978-04-11 | Robert Bosch Gmbh | Fuel injection pump for internal combustion engines |
US4351283A (en) * | 1981-05-01 | 1982-09-28 | General Motors Corporation | Diesel fuel injection pump secondary fuel metering control system |
US4458649A (en) * | 1981-03-11 | 1984-07-10 | Hitachi, Ltd. | Fuel injection pump for internal combustion engines |
US4492534A (en) * | 1982-10-05 | 1985-01-08 | Nippondenso Co., Ltd. | Fuel injection pump for internal combustion engine |
US4497298A (en) * | 1984-03-08 | 1985-02-05 | General Motors Corporation | Diesel fuel injection pump with solenoid controlled low-bounce valve |
US4501246A (en) * | 1981-07-22 | 1985-02-26 | Robert Bosch Gmbh | Fuel injection pump |
US4598683A (en) * | 1984-03-15 | 1986-07-08 | Nippondenso Co., Ltd. | Fuel injection pump of the distribution type |
US4655184A (en) * | 1981-06-12 | 1987-04-07 | Robert Bosch Gmbh | Fuel injection apparatus for internal combustion engines |
US4767288A (en) * | 1981-06-11 | 1988-08-30 | Robert Bosch Gmbh | Fuel injection pump |
US5099814A (en) * | 1989-11-20 | 1992-03-31 | General Motors Corporation | Fuel distributing and injector pump with electronic control |
US5353766A (en) * | 1993-09-08 | 1994-10-11 | Cummins Engine Company, Inc. | Distributor for a high pressure fuel system |
US5678521A (en) * | 1993-05-06 | 1997-10-21 | Cummins Engine Company, Inc. | System and methods for electronic control of an accumulator fuel system |
US5983863A (en) * | 1993-05-06 | 1999-11-16 | Cummins Engine Company, Inc. | Compact high performance fuel system with accumulator |
US20140026854A1 (en) * | 2011-04-15 | 2014-01-30 | Husqvarna Ab | Carburetor system for a carburetor engine |
US20160245084A1 (en) * | 2015-02-20 | 2016-08-25 | Vianney Rabhi | Distributer phase shifter for a hydraulic pump motor |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1577918A (en) * | 1976-04-20 | 1980-10-29 | Lucas Industries Ltd | Liquid fuel pumping apparatus |
US4426983A (en) * | 1980-10-04 | 1984-01-24 | Lucas Industries Limited | Liquid fuel pumping apparatus |
US4367715A (en) * | 1980-12-17 | 1983-01-11 | The Bendix Corporation | Distribution injection pump for diesel engines |
DE3148688A1 (en) * | 1981-12-09 | 1983-06-16 | Robert Bosch Gmbh, 7000 Stuttgart | DEVICE FOR GENERATING A FUEL QUANTITY SIGNAL |
EP0087119A3 (en) * | 1982-02-17 | 1983-10-05 | Hitachi, Ltd. | Fuel injection pump |
JPS5920558A (en) * | 1982-07-26 | 1984-02-02 | Hitachi Ltd | Fuel metering and supplying device of injection pump |
DE3243348A1 (en) * | 1982-11-24 | 1984-05-24 | Robert Bosch Gmbh, 7000 Stuttgart | FUEL INJECTION PUMP |
DE3248713A1 (en) * | 1982-12-31 | 1984-07-05 | Robert Bosch Gmbh, 7000 Stuttgart | METHOD FOR INJECTION OF FUEL AND FUEL INJECTION DEVICE FOR CARRYING OUT THE METHOD |
DE3612942A1 (en) * | 1986-04-17 | 1987-10-22 | Bosch Gmbh Robert | FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3476050A (en) * | 1967-04-17 | 1969-11-04 | Cav Ltd | Liquid fuel pumping apparatus |
US3482519A (en) * | 1967-03-28 | 1969-12-09 | Cav Ltd | Liquid fuel pumping apparatus |
-
1969
- 1969-04-18 DE DE19691919707 patent/DE1919707A1/en active Pending
-
1970
- 1970-03-26 US US22883A patent/US3598507A/en not_active Expired - Lifetime
- 1970-04-20 FR FR7014250A patent/FR2045502A5/fr not_active Expired
- 1970-04-20 GB GB1870170A patent/GB1310386A/en not_active Expired
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3482519A (en) * | 1967-03-28 | 1969-12-09 | Cav Ltd | Liquid fuel pumping apparatus |
US3476050A (en) * | 1967-04-17 | 1969-11-04 | Cav Ltd | Liquid fuel pumping apparatus |
Cited By (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4083346A (en) * | 1975-01-28 | 1978-04-11 | Robert Bosch Gmbh | Fuel injection pump for internal combustion engines |
US4458649A (en) * | 1981-03-11 | 1984-07-10 | Hitachi, Ltd. | Fuel injection pump for internal combustion engines |
US4351283A (en) * | 1981-05-01 | 1982-09-28 | General Motors Corporation | Diesel fuel injection pump secondary fuel metering control system |
US4767288A (en) * | 1981-06-11 | 1988-08-30 | Robert Bosch Gmbh | Fuel injection pump |
US4655184A (en) * | 1981-06-12 | 1987-04-07 | Robert Bosch Gmbh | Fuel injection apparatus for internal combustion engines |
US4501246A (en) * | 1981-07-22 | 1985-02-26 | Robert Bosch Gmbh | Fuel injection pump |
US4492534A (en) * | 1982-10-05 | 1985-01-08 | Nippondenso Co., Ltd. | Fuel injection pump for internal combustion engine |
US4497298A (en) * | 1984-03-08 | 1985-02-05 | General Motors Corporation | Diesel fuel injection pump with solenoid controlled low-bounce valve |
US4598683A (en) * | 1984-03-15 | 1986-07-08 | Nippondenso Co., Ltd. | Fuel injection pump of the distribution type |
US5099814A (en) * | 1989-11-20 | 1992-03-31 | General Motors Corporation | Fuel distributing and injector pump with electronic control |
US5678521A (en) * | 1993-05-06 | 1997-10-21 | Cummins Engine Company, Inc. | System and methods for electronic control of an accumulator fuel system |
US5983863A (en) * | 1993-05-06 | 1999-11-16 | Cummins Engine Company, Inc. | Compact high performance fuel system with accumulator |
US5353766A (en) * | 1993-09-08 | 1994-10-11 | Cummins Engine Company, Inc. | Distributor for a high pressure fuel system |
US20140026854A1 (en) * | 2011-04-15 | 2014-01-30 | Husqvarna Ab | Carburetor system for a carburetor engine |
US11131271B2 (en) * | 2011-04-15 | 2021-09-28 | Husqvarna Ab | Carburetor system for a carburetor engine |
US20160245084A1 (en) * | 2015-02-20 | 2016-08-25 | Vianney Rabhi | Distributer phase shifter for a hydraulic pump motor |
US10632829B2 (en) * | 2015-02-20 | 2020-04-28 | Vianney Rabhi | Distributer phase shifter for a hydraulic pump motor |
Also Published As
Publication number | Publication date |
---|---|
DE1919707A1 (en) | 1970-11-12 |
GB1310386A (en) | 1973-03-21 |
FR2045502A5 (en) | 1971-02-26 |
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